Roller bearing



.'5 Sheets-Sheet l HHH J. O. HEINZE ROLLER BEARING Filed Jan. 19, 1938 April 16, y1940.

J. o. HElNzE 2,197,499 RoLLER BEARING Filed Jan. 19, 1938 3 Sheets-Sheet 2 Gftornegs April 16, 1940. J. Q. HElNzE ROLLER BEARING yFiled Jn. 19, 1938 s sheets-sheet s 'ZZ i Patented pr. i6, i940 NIT ED s'ra'rrisv 2,197,499 ROLLER BEARING .reim o. Heinze, Detroit, Mien., assigner te Heinze Development Company, Detroit, Mich., acorpor'ation of Michigan Application `lianuary 19, 1939, Serial No. 185,689 Claims. (Cl. 308-180) This invention relates to improvements in journal bearings and pertains more particularly to assemblages of this type designed for service under heavy load conditions-illustrated for in- 5 stance, by service in the axle or journal boxes of railway cars, engines, etc., although usable under less onerous conditions.

The roller bearing according to the present invention comprises inner and outer race mem-l bers and a plurality of rollers in spaced relation within the race, one of said race members having bearing contact with a roller within a zone central of the length of said roller and the other race member having bearing contact with said roller li5 in two zones spaced one at each side of the central zone, and it is characterized in that vthe distance between the central zone and each of suflicient to provide leverage characteristics and to cause the roller axis to be deflected from its normal position when the roller is subjected to loads above a predetermined value, whereby the load is distributed over a plurality of adjacent rollers, the rollers and race members being so designed as to allow said rollers to deflect and means being provided to limit this deliection. In addition, the assembly permits a-compensating effect designed to meet the conditions of deflection. This is brought about by arranging the raceway for each contact point as a convex surface on a cross-section of the race member, the opposing faces of roll and race surface thus presenting a ltangential eiect. As a result, the several contacts, with no roll defiection, will be point contacts with a maximum spacing between suchv points. As. the roll deflects, the central point becomes of zonal type linear of the roll, with the zone length increasing with the vdeliection value increase; at the same time the roll 4,0 deflection will tend to cause the respective end zones of the roll to shift the point of contact on the individual race surface in a direction to decrease the spacing distance of the two points of contact.

In addition, the' assembly provides a safety factor of importance. The bearings include means for meeting thrust conditions, this being in the form of a pair of raceways for balls, each of these raceways being` located but spaced from 5U an end. of the roll, and serving to resist thrust action of the bearing.

Hence, the-bearing assembly provides for the Adeflection characteristics within a range which generally represents the normal operations of the car or engine, but in presenceo an abnormal condition whichcould be damaging in effect, the bearing adds the efect of a ball bearing of unyielding type.

The advantage of this lies in the fact that during normal operation the kload is being sup- 5 ported on the basis of the roll support with the relative yield such as ensures that the load is being distributed through a plurality of rolls at all times, and yet provides a limit beyond which the yield effect cannot pass, regardless of service 10 conditions.

The bearing assembly of the present invention is therefore an assembly designed particularly to meet the extremely onerous conditions of heavy load activities and under service condi- 15 tions extremely onerous,l doing this by ensuring at all times a load distribution over a plurality of rolls even when the latter have the usual manufacturing allowances to meet the heavy load duty, and at the same time provide a bearing 20 which will automatically compensate for the inevtable axle expansion when braking, hammer blow effects set up by track conditions, elimination of noise, etc. I

To these and other ends therefore, the nature 25 of which will be made more apparent as the in vention is hereinafter described in detail, this invention consists in the construction and arrangement of elements. and parts all as hereinafter disclosed in the following description, 30 illustrated in the accompanying drawings, and more particularly pointed out in the appended claims.

In the accompanying drawings, in which sim, ilar reference characters indicate similar parts 35 in each of the views:

Figure l is a vertical section through an axle box or journal of a heavy-duty assemblage, the section being taken on line I-I of Fig. 3;

Fig. 2 is a horizontal section of the same, taken 40 on the line 2--2 of Fig. l;

Fig. -3 is a view, partly in section and partly in elevation taken in the direction lof the axis of the axle;

Fig. 4 is a side elevation of a car truck, the 45 bearings of which include the present invention;

' JFig. 5 is a detail sectional view taken on line 5-5 of Fig. .4;

Fig. 6 is a view taken on line E-G of Fig. 2;'

Fig. 'l is a view illustrating the conditions set 50 up by a deection of a roll with one type of raceway faces;

Fig. 8 is a view similar to Fig. 'l but with the raceway faces arranged in accordance with the preferred form of the present invention; 55

Fig. 9 is a detail perspectiveview of the journal internal space to receive the axle end and bearbox closure; ing assembly. The'upper portion of the housing Fig. 10 is a fragmentary sectional view showis formed with a large recess I8, closed by a ing a modied arrangement of the three-point removable plate I9, the recess being designed to bearing; receive a supply of lubricant for the bearing, the i Fig. 11 is a fragmentary detail section on an recess having a plurality of ports 20 extending enlarged scale, showing the leverage characteristhrough its bottom wall into the bearing receivroll deflection, and' y e ou Fig. 12 is a view similar to Fig. 1I, illustrating tions 2|, 2|, these being substantial duplicates, 11

more particularly to meet the conditions of underlying' the meeting line of the two sections. 16

conventional truck of this type with the invenlocation of these zones, with the result that the with resultant development of heat; with the stance, in Fig. 2 the roll contact midway of its 30 nectionare not presented herein since they are ditions are reversed, the outer race member conthe temper of the metal; in addition, the axle used. For instance, in the form of Fig. 2, the

surface contact with the axle, but which have a. roll. The end walls of the recess thus formed @rating Speeds, but, due t0 llmted 'Surfaee COH- of such raceways; as indicated in Figs. 8, 11 and tact, heat dissipation iS less rapid with the result 12, these raceways each have the active face as ditions; it is the practice, where rolls are used, is practically that of a point contact, the partO provide the assembly 8S Sloppy in Order t0 ticular location of the point being dependent reduce the eiTect of the expansion on the rolls upon the deflection value of the rol] at any `tends to the creation of noise; and even with this While not; limited to such form, the roll 23 form the speed maximum is reduced, due to the is itself shown as of the two-diameter type, with at higher Speeds, and With limited dissipation cf This type not only provides for slower planeting are Well known, and-tend t0 limit speedsin 0pcated at the ends of the roll central zone, extenderation to values such that the needed braking ing into the space 2lb, and surrounding the 65 friction Will remain Within limits such as to smaller diameter zone. Rolls of uniform diameprevent axle expansion beyond limits permitted ter may be utilized,'however, in which case the by loose'roll assembly. anti-creeping means is of a somewhat diierent As indicated in Figs. 1, 2 and 3, the axle hous` type. ing is formedI sectional, and comprises an inner Beyond the` roll zone of the composite outer cured together, face to face vby bolts or other bearing zone, with the latter designed to operate securing means l1 (Fig. 1) so as to form an normally to resist thrust conditions. To enable u roll deflection, however, the raceway is arranged in the properpositions. A locking pin 26a serves to permit suflicient movement of the race meinto hold the members in position.

bers relative 'to leach other within predetermined The axle also carries an axial lubricant paslimits before the ball contacts with the race on sage within a chamber having lateral outletsinto the race face corresponding to a radius of the i the bearing zones. Any. suitable closure means 5 bearing, the race face in the thrust direction for this supply may be employed, the drawings having the usual characteristic, with the ball indicating a s mple arrangement in the form of cage being properly arranged to maintain the a tubular structure 21 extending outwardly from ball positions under this change from the usual the axle end into an opening in the outer housing 1 formation of ball raceways. l member i6, and having a supply opening nor- 10 it will be noted .that the assembly including molly Closed by e cheekfvalve in the form of a the inner or outer-races; the rolls, balls and their ball 2M- races, forms a bearing unit for the support of AS indeated, suitable dust-excluding structhe axle end within the journal box, and that' tures areempleyed at desired points. 5 this unit centersthe axle end or journalwithin AS indloated above, an underlying feature of 15 Jehe box iongirudineny thereof by forming the the present invention is the fact that the rolls outer raceway with an exterior annular projecare SllPlJOted 1n 511011 manner as t0 permit a tion lla which is provided with an outer surface C0nt10lled Yield elatOnShiP between the axle curved'longitudinally of the axle to flt within and the load-Carrying Super-structure, this rean interior groove in the parte |5...| 'of the sult being obtained by deflection of rolls, with 20 box, and therefore the unit assembly is movable, the deflection Changing the roll axis from a upon binding movement of the axle as a'whole, Straight line to approximately a curved line about a central point or axis of the foi-mation of characteristic. To provide this result, the race the curved surface of the annular projection. faces are arranged along the lines of a three- 25 Referringto Fig. 2, the inner race member PUDV mounting f01` the T011, With tWo of the 25 2t is also acomposite member, the two sections, 13F SPaCed apart 0n one side oi the roll, the however being of dissimilar communi-,ione In third point being on the opposite side of the roll this form the central zone of the roll is in eon- Intermediate the two spaced points. Obviously, taci-, with the inner race member, and hence to permit a deiiection action of the rolls, without the rece face 245g, is foi-med mtegrai with the danger of roll-shearing eiects, it is essential 3o inner seetion of ine member, end, like the reee that the spacing of the points of Contact be faces of the outer member, this face is 'prefer- Sufficient 94S t0 Provide this action, and, at the ably made convex. As indicated in Figs. l1 and Same time, Set UD tile proper leverage conditions 12, this latter arrangement sets up the charas lllllstrated m Figs. ll-12` which will enable eeierist'io of-e, point Contact with the eem-,rei proper control of the deection. As it is appar- 35 zone of the foil in the absence of -defieetien of ent that the greater thedistance between points the letter, but when roll'derleetion is present this the, greater becomes the levereee velue and less point iengthens out into a iineV Zone the length resistance by the roll, the particular distance be- `of which is determined by the deiiection value. tween PO'ntS Will .depend Upon the Conditions rece member and es Weil as the Outeiseei-,ien bearing dimensions are more or less individual have coniigurations to provide theA complemental t0 the Particular Condltlons t0 be met race faces for the thrust ball bearings. The in- It ha been found that if the asembly iS Aner mee member is cai-fied by the axle formed in such manner that a roll will deflect lef the three .001" for each 2000 pounds oi load beyond a 45 lin the form of Fig. 10, the reversa nson laces the central Oint of com minimum load, the best results will be obtained; pomt suspe 1 p p such deection values will permit car loadings to tact as with the outer race member-in winch case the annular ymember 2in, presents the race n qaumum cafaclty and s n be Wthm safety lace, the latter being convexed. 'Since the inner hmltsg Tms 1S n ade possble throilgh the fact race member now provides the tWo spaced point that, since deflection of rolls is possible, the load contact, the two sections can be substantial Weight 1S distnbute@ wel: a mummy of Tous" duplicates, the two race-faces for the rollsbeing m an assembly havmg elghteen Tous the load becomes distributed over seven of them, with properly located to'produce the desired result, with eaclr face convexed. In this form, the ball each 011-ta'kmg a Share 0f the 10mi We1ght raceways can be varied'from the form of Fig. 2, thus causmg each of the active Tous to be de' 55 with the outer race member presenting the norected, concurrently v th eac@ You preentng mal relationship with the bau and with the its resistance to deiiectlon to aid the resistance raceway of theinner race-member arranged with Value of adlant Tous' cnsequenmy .the heavy the 'deection-permtting space referred to. Weights presented 1n.ra11wa S.e.rv1 can be The race members are held in position by Suit? adequately cared for without liability of damag- 6e able locking, mechanism carried by the ena of ing the rolls, since the rolls cannot reach a F t th nd f th ,l tte 1 straining point due to the presence of the deyalvxa gdlcsengro eb' vhiehe isa ex flection-limltlng feature set up by the ball bearternally threaded, and designed to receive a gct lfsl ggdttgttltStgtgltan two-part col1af25, 26, the former being internalthis .range of deflection Wm meet the various ly threaded and havingv a conical external race, Service conditions even when abnormal the the membe 25 bemg annular' but 59kt and valuesabove indicated as a basis for dimensionhaving an internal face complemental to the ing the bearing are deemed preferable Z@ conical falce tof member 25. When the bearing As is apparent the Contact between a you and is assembled in position, member 25 iS brught is raceways is such that leverage llaracteristics m OIltaCt With the Outer SeCtllOll 0f the inner -are present 01- possible ai', all times, due t() the race membeL-a'iter which member 25 is threaded spacing ofthe contact points lengthwise of the toits position, the 'opposing conical feces serving roll. The maximum length oi' line of contact im to move member `2 6 to locate the bearing parts of the single contact side of the roll is always 75 40 The. end zene of the inner section of the inner which the bearing is to meet. Consequently, the ,m

whether of uniform diameter or of two or more resistance follows the initial change so that the 10 the different types; but in any case the spacing The maximum resistance to deflection is 1B issuch as to set up the leverage characteristic reached as the roll deflection of the bearing 15 preferred that such faces be convex instead of begin to-functlon as load-sustaining structures, 20

have a line contact with the spaced race facesv vision for the factors of axle expansion and of 30 On the contrary, in the form of Fig. 8, in which same time provide'for sturdy construction to aid 35 11e with the contact point at the @PSX'O the COU- the underlying 'principles of the invention can 40 within the spirit and scope of the invention as -serve to vary the leverage value, as is indicated 1 In J0.u.mal bearings for service mder heavy A between those indicated and outer race members, a pluralitydof rolls 1n In' other words, with the deflection of the roll at zero value, the leverage conditions present bers combmedly presentmghannular track su!" roll- La As dection proceeds the leverage con central of'the length of the roll and a bearing 65 of deectionand therefore more sensitive-t0 the videleverage characteristics between the central 70 central zone of a roll and active automatically `as supplementing load-sup- .v

porting bearings in presence of a predetermined deflection value of the rolls to thereby limit the range -of roll deection in presence of abnormal service conditions.

2. In journal bearings for service under heavy load conditions, wherein the bearing is formed to support the load with the load distributed over a plurality of adjacent rolls to provide a load support of zonal characteristic under normal,

running conditions, the combination of, inner and outer race members, a plurality of rolls in spaced relation within the race, said race members combinedly presenting annular track surfaces within the race to provide bearing contact of a roll with one of said members within 'a zone central of the length of the rollend a bearing contact of the roll with the other member in a pair of zones spaced apart a distance suflicient to locate each zone of the pair as lying outside o f such central zone a distance suflicient to provide leverage characteristics between the central zone and each of the pair of zones to thereby cause the roll axis to be varied from its repose status by roll deiiection in presence of predetermined load values and thereby distribute load application over a' plurality of adjacent rolls with the deflection value of the respective rolls of the load-supporting zone decreasing towards the end of such load-supporting zone, and means in the form of 'member faces forming portions of the race member assembly with such faces co-operative to produce a pair of ball thrust raceways respectively lying outside of the roll race, with one ball race face normally inactive with the balls of the ball bearing in direction radially of the bearing but movable into ball contact for activity to sustain load weight in presence of roll deflection of predetermined value to thereby limit the range of roll deflection.

3. In journal bearings for service under heavy load conditions, and in combination, inner and outer racemembers, and a plurality of rolls in spaced relation within the race, said race members combinedly presenting annular track sur faces contacting the rolls at spaced locations in the length of the rolls with the spacing-such as to provide leverage characteristics between the the end zones of such roll, the leverage'being substantially symmetrical on opposite sides of the mid point in the roll length, whereby load values beyond a predetermined minimum valuevwill product deflection of the roll within the roll length, said track surfaces havingl a lcross-sectional contour varied from the roll contour 'opposing each surface to thereby cause variationsl in leverage values by variations, in roll deflection values, the leverage variations being indirections to decreasev the leverage value as the deflection value increases and to increase leverage values as the deflection values decrease, the bearing including a pair of thrust ball races normally inactive to affect roll deection but rendered active in supplementary supporting the load by roll deection of predetermined value to thereby limit the range of roll deection.

4. In journal bearings for service under heavy load conditions, and in combination, innerand outer race members, and a plurality of rolls in spaced relation within the race, said race members combinedly presenting annular track sur-v faces contacting the rolls at spaced locations in the length of the rolls with the spacing such as to provide leverage characteristics betweenthe central zone of a roll and the end zones of such roll, the leverage being substantially symmetrical on opposite sides of the mid point in the roll length,whereby load values beyond a predetermined minixnum value will produce deflection 0f the roll within the roll length, said'track surfaces having a cross-sectional contour varied from the roll contour opposing each surface to thereby cause variations in leverage values by variations in roll deflection values, the leverage variations being in directions to decrease the leverage value as -the deflection value increases and to increase leverage values as the deiiection values decrease', the bearing including a pair of thrust ball races normally inactive to affect roll deection but rendered active in supporting the load by lroll deflection of predetermined value to thereby limit the range of roll deflection,such supplemental load-support activity of the thrust Vbearings serving to provide the minimum limit to the rangev of leverage values.

5. In antifriction bearings for the axles of railway rolling stock, wherein the bearing is formed 'to support the load with the load distributed over a'plurality of adjacent rolls to provide a load support of zonal characteristic under normal running. conditions, the combination of, a sectional housing for receiving an end of the wheel axle, an inner racel member carried by such axle end, an outer race member Within the housing, relation within the race, said race members combinedly presenting annular track surfaces Within the race to provide bearing contact of a roll with one of said members within a zone central of the length of the roll and a bearing contact of the rolll with the .other member in a pair of zones spaced apart a distance sufficient to provide leverage characteristics between the central zone and each of the pair of zones, whereby load values beyond a predetermined minimum value will produce deection of the roll within the roll length, said members having ball-race faces to receive the balls of a pair of ball bearings operative as thrust bearings, said ball-race faces including conflgurations adapted to normally render the balls inactive in supporting the load but adapted to be rendered active in such load support in presence of a predetermined deflection value of the rolls.

JOHN 0. HEINZE.

and a plurality of rolls in spacedv 

